Refrigerating storage cabinet

ABSTRACT

A storing section  49  stores data of a pull down cooling characteristic indicative of a time-varying mode of reduction in a target temperature drop. For example, when this is a linear function line xp, a target internal temperature drop degree takes a constant value Ap, irrespective of an operating time. An actual temperature drop degree Sp is computed on the basis of the detected internal temperature. The computed value Sp is compared with a target value Ap read from the storing section  49.  When the computed value Sp is less than the target value Ap, a rotational speed of an inverter compressor  32  is increased via an inverter circuit  55.  When the computed value Sp is larger than the target value Ap, the rotational speed of the compressor  32  is decreased. The speed increases and decreases are repeated so that pull down cooling is performed along the linear line xp.

TECHNICAL FIELD

The present invention relates to a refrigerating storage cabinet, andmore particularly, to a refrigerating storage cabinet with an improvedcontrol of refrigerating operation.

BACKGROUND ART

Refrigerators for commercial use have recently been provided with aninverter compressor so that the refrigerating performance is adjustedaccording to the load (see patent document 1, for example).

Refrigerators provided with an inverter compressor of this type carryout their highest allowable speed operation in pull down cooling.However, large, middle, and small heat insulating housings present cleardifferences among the internal temperatures when pull down cooling isperformed under identical conditions in which food is not accommodatedin the compartments, as shown in FIG. 26. The reason for this is thatthe difference in the degree of temperature drop is proportional to thesurface area of the heat insulating housing, when the difference in theinternal and external temperatures is the same. In addition, the heatcapacity of an internal wall material or rack is significant as the boxbecomes larger.

DISCLOSURE OF THE INVENTION Problem to be Overcome by the Invention

On the other hand, greater importance is placed on the temperaturecharacteristic of pull down refrigeration in commercial userefrigerators-freezers. For example, refrigeration starting from a highinternal temperature, such as 20° C., is substantially limited to aninitial operation after installation, re-operation several times afterpower-off for maintenance, several minutes of door opening in theaccommodation of food materials, or the accommodation of hot food. Inthe refrigerators-freezers for commercial use, doors are frequentlyopened and closed so that food materials are placed into and taken outof compartments where the ambient temperature is relatively higher. Inview of these reasons, it should be taken into sufficient considerationthat the internal temperature easily rises. Accordingly, a temperaturedrop characteristic should be considered as a returning force in theinternal temperature rise.

Accordingly, a performance test for pull down refrigeration iscompulsory. However, the performance test needs to be conducted with therefrigeration units having been assembled to the heat insulatinghousings. As a result, there is a problem of inconvenience andcomplication, such as the problem in which the places where and thetimes when a test should be conducted are limited.

The present invention was made in view of the foregoing circumstances,and an object thereof is to be able to refrigerate the inner atmosphereaccording to a predetermined refrigeration characteristic.

Means for Overcoming the Problem

As means for achieving the above object, the invention of aspect 1 is arefrigerating storage cabinet in which an inner atmosphere isrefrigerated by a refrigeration unit, including a compressor and anevaporator. This is characterized in that the compressor is of avariable performance type. In addition, this is characterized by storingmeans for storing data of a cooling characteristic indicative of atime-varying mode of a reduction in a target physical amount associatedwith cooling, such as an internal temperature, and also by operationcontrol means for varying the performance of the compressor on the basisof the output of a physical amount sensor detecting the physical amountso that the physical amount is reduced by following the coolingcharacteristic read from the storage means.

The invention of aspect 2 is characterized in that in aspect 1 the inneratmosphere is modified to be refrigerated to a predetermined settemperature. The cooling characteristic is a pull down coolingcharacteristic associated with a pull down cooling zone, which is atemperature zone from a high temperature, apart from the settemperature, to near the set temperature.

The invention of aspect 3 is characterized in that in aspect 1control-cooling is modified to be performed. The compressor is operatedwhen the internal temperature has reached an upper limit temperature,higher by a predetermined value than the set temperature. The compressoris stopped when the internal temperature has reached a lower limittemperature, lower by a predetermined value than the set temperature.The compressor is repeatedly operated and stopped so that the inneratmosphere is maintained about the set temperature, wherebycontrol-cooling is performed. The cooling characteristic is acontrol-cooling characteristic associated with the control-cooling zone.

The invention of aspect 4 is characterized in that, in any of theaspects 1 to 3, the compressor is a speed-controllable invertercompressor. The operation control means comprises a physical amountchange computing section computing a reduction degree of the physicalamount on the basis of a signal of the physical amount sensor at eachpredetermined sampling time. A target physical amount reduction degreeoutput section provides a target physical amount reduction degree in thephysical amount at the sampling time, on the basis of the coolingcharacteristic stored in the storage means, at every sampling time. Acomparing section compares the actual physical amount reduction degreecomputed by the physical amount change computing section with the targetphysical amount reduction degree produced by the target physical amountreduction degree output section. A speed control section controls theinverter compressor so that the speed of the inverter compressor isincreased when the actual physical amount reduction degree is smallerthan the target physical amount reduction degree, and so that the speedof the inverter compressor is decreased when the actual physical amountreduction degree is larger than the target physical amount reductiondegree, based on the results of a comparison by the comparing section.

The physical amount reduction degree is defined as an amount ofreduction in the physical amount per unit of time.

The invention of aspect 5 is characterized in that in aspect 4 therefrigerating characteristic is represented as a linear functioninvolving a physical amount and time. The target physical amountreduction degree output section provides the target physical amountreduction degree as a constant value.

The invention of aspect 6 is characterized in that in aspect 4 therefrigerating characteristic is represented as a quadratic functioninvolving a physical amount and time. The physical amount reductiondegree output section computes a physical amount reduction degree in thephysical amount at every sampling time, providing a computed value basedon the quadratic function as the target physical amount reductiondegree.

The invention of aspect 7 is characterized in that in aspect 4 therefrigerating characteristic is represented as an exponential functioninvolving a physical amount and time. The physical amount reductiondegree output section computes a physical amount reduction degree in thephysical amount at every sampling time, providing a computed value basedon the exponential function as the target physical amount reductiondegree.

The invention of aspect 8 is characterized in that in aspect 4 areference table is previously made so as to place a physical amount anda target physical amount reduction degree into a correspondence witheach other on the basis of a cooling characteristic. The target physicalamount reduction degree output section has a function of retrieving andproviding the target physical amount reduction degree corresponding tothe current physical amount in the reference table.

The invention of aspect 9 is characterized in that in aspect 4 the inneratmosphere is modified to be refrigerated to a predetermined settemperature. The cooling characteristic is a pull down coolingcharacteristic associated with a pull down cooling zone, which is atemperature zone from a high temperature, apart from the settemperature, to near the set temperature. At a first half side of thepull down cooling zone, the pull down cooling characteristic isrepresented as a linear function involving a physical amount and time,and the target physical amount reduction degree output section providesthe target physical amount reduction degree as a constant value. At asecond half side of the pull down cooling zone, the pull down coolingcharacteristic is represented as a quadratic function involving aphysical amount and time, and the target physical amount reductiondegree output section computes the physical amount reduction degree inthe physical amount at every sampling time, providing a computed valuebased on the quadratic function as the target physical amount reductiondegree. Alternatively, a reference table is previously made so as toplace a physical amount and the target physical amount reduction degreeinto a correspondence with each other on the basis of a coolingcharacteristic. The target physical amount reduction degree outputsection has a function of retrieving and providing the target physicalamount reduction degree corresponding to the current physical amount inthe reference table.

The invention of aspect 10 is characterized in that in aspect 4 aplurality of programs are provided that vary the performance of thecompressor so that a physical amount associated with cooling, such as aninternal temperature, is reduced following a predetermined coolingcharacteristic. The programs have different cooling characteristicswherein each program is selectively stored in a control means, providedin the refrigeration unit, so as to be executable.

The invention of aspect 11 is characterized in that in aspect 2 aplurality of target pull down cooling characteristics is provided. Eachpull down cooling characteristic is selectively readable according to acondition or the like.

The invention of aspect 12 is characterized in that in aspect 11 one ofthe pull down cooling characteristics is selectable according to thezone of the physical amount associated with cooling, such as an internaltemperature.

The invention of aspect 13 is characterized in that in aspect 11 eachpull down characteristic is indicative of a time-varying mode ofreduction in temperature. The condition is the difference between theset temperature and an actual internal temperature. The pull downcooling characteristic with a relatively smaller degree of temperaturedrop is selected when the difference is less than a predetermined value.The pull down cooling characteristic with a relatively larger degree oftemperature drop is selected when the difference is above thepredetermined value.

The degree of temperature drop is defined as the amount of temperaturedrop per unit of time.

The invention of aspect 14 is characterized in that in aspect 13 one ofthe pull down cooling characteristics is an auxiliary coolingcharacteristic with a temperature curve in which a convergencetemperature remains at a temperature, higher than the set internaltemperature by a predetermined value. The auxiliary coolingcharacteristic is selected when a difference between the internaltemperature and the evaporation temperature of the evaporator is at orabove a predetermined value, or when the internal temperature is apartfrom a target temperature by a predetermined value or above.

The invention of aspect 15 is characterized in that in aspect 1 pulldown cooling is performed in which an inner atmosphere is cooled from ahigh temperature apart from the set temperature, to near a settemperature. Control-cooling is performed in which the compressor isoperated when the internal temperature has reached an upper limittemperature, higher by a predetermined value than the set temperature.The compressor is stopped when the internal temperature has reached alower limit temperature, lower by a predetermined value than the settemperature. The compressor is repeatedly operated and stopped so thatthe inner atmosphere is maintained about the set temperature. Withregard to a pull down cooling zone, the storing means stores the data ofa pull down cooling characteristic indicative of a time-varying mode ofreduction in a target physical amount associated with cooling, such asan internal temperature. The performance of the compressor is varied onthe basis of the output of a temperature sensor, detecting the internaltemperature, so that the internal temperature is reduced following acooling characteristic read from the storing means. With regard to acontrol-cooling zone, the performance of the compressor is varied sothat the internal temperature is reduced from the upper limittemperature to the set temperature by following the pull down coolingcharacteristic read from the storing means. The operation control meansis provided for decreasing the performance of the compressor after theinternal temperature has reached the set temperature.

The invention of aspect 16 is characterized in that in aspect 1 theoperation control means has a function of increasing the performance ofthe compressor when the internal temperature has reached the settemperature and rises again, after a reduction in the performance of thecompressor.

EFFECT OF THE INVENTION

<The Invention of Aspect 1>

The storing means previously stores data of a cooling characteristicindicative of a time-varying mode of reduction in a target physicalamount. In refrigerating operation, the cooling characteristic is readfrom the storing means. The performance of the compressor is controlledso that a physical amount detected by the physical amount sensor isreduced following the cooling characteristic read from the storagemeans.

More specifically, the inner atmosphere is refrigerated according to apredetermined cooling characteristic irrespective of the conditions suchas the capacity of the heat insulating housing. The coolingcharacteristic is optionally settable with a wide range such as the onein which a reduction in the physical amount changes from moment tomoment.

<The Invention of Aspect 2>

The inner temperature rises to a large extent with the opening of thedoor. With regard to pull down cooling reducing the raised temperatureto a set temperature, a pull down cooling characteristic is previouslystored that is indicative of a time-varying mode of the reduction in atarget physical amount. The performance of the compressor is controlledso that the corresponding physical amount is reduced following the pulldown cooling characteristic.

In other words, pull down cooling is performed according to apredetermined pull down cooling characteristic, irrespective ofconditions such as the capacity of the heat insulating housing.Accordingly, the performance test in pull down cooling has no relationwith an actually used heat insulating housing to which the refrigerationunit is attached. For example, a test heat insulating housing can beused for the performance test. Consequently, the degree of freedom inthe place and time of the performance test can be increased to a largeextent.

<The Invention of Aspect 3>

The performance of the compressor is controlled so that thecorresponding physical amount is reduced following the control-coolingcharacteristic during the operation of the compressor incontrol-cooling. When the control-cooling characteristic is set at agentle gradient, the cooling can be carried out while the compressor isin low performance operation, namely, while energy savings are achieved.On the other hand, when the control-cooling characteristic is suitablyset at a lower limit temperature, the operation of the compressor canreliably be stopped, whereby a defrosting operation is performed in theevaporator. Accordingly, a large amount of frost can be prevented.

<The Invention of Aspect 4>

In the cooling operation, an actual physical amount reduction degree isobtained on the basis of the detected physical amount, while a targetphysical amount is produced from the data of the cooling characteristic.The inverter compressor is controlled so that the speed of the invertercompressor is increased when the actual physical amount reduction degreeis less than the target physical amount reduction degree. In a contrarycase, the inverter compressor is controlled so that the speed of theinverter compressor is decreased or the inverter compressor is stopped.The control is repeated so that the inner atmosphere is cooled accordingto the predetermined cooling characteristic.

<The Invention of Aspect 5>

Since the target physical amount reduction degree is constantirrespective of a lapse of time, calculation is not required.Accordingly, the control system can be simplified.

<The Invention of Aspect 6>

The cooling characteristic is represented as a quadratic functioninvolving a physical amount and time. A target physical amount reductiondegree is computed from the quadratic function as an amount of reductionin the physical amount per unit of time at every sampling time. Forexample, a temperature drop characteristic that has had realaccomplishments in the market and has earned a fine reputation from itsusers can be used as the target temperature drop characteristic in pulldown cooling.

<The Invention of Aspect 7>

The refrigerating characteristic is represented as an exponentialfunction involving a physical amount and time. A target physical amountreduction degree is computed from the exponential function as an amountof reduction in the physical amount per unit of time at every samplingtime. For example, when the temperature in the heat insulating housingdrops due to heat radiation, in many cases the temperature change isapproximated by the curve of an exponential function. Consequently, atemperature drop characteristic can be used in keeping with the actualtemperature drop.

<The Invention of Aspect 8>

The target physical amount reduction degree corresponding to a currentphysical amount is retrieved and provided to the reference table atevery sampling time. A physical amount reduction characteristic of anapproximate quadratic function is applicable. A target physical amountreduction degree is obtained only by referring to the reference tableand no calculation is required. Consequently, the control speed can beincreased.

<The Invention of Aspect 9>

For example, in a refrigerator with a set internal temperature of 3° C.,it is rare that the internal temperature rises to 15° C. or 20° C., eventhough the door is frequently opened and closed or a large amount ofwarm food material is placed within the refrigerator. It is the zone ator lower than 20° C. or 15° C. that requires a returning force. In thiszone, rapid refrigeration following a pull down cooling characteristicof a quadratic function is desirable. However, when a quadratic functionis applied to a zone at or higher than 20° C. or 15° C. (first half ofthe pull down cooling), a large cooling performance is required.Accordingly, an inverter compressor able to cope with high-speedrotation or an evaporator with a large capacity is required. In otherwords, in order to cope with the first half of pull down cooling, whichhas a low frequency of occurrence and is less important, providing theabove inverter compressor or evaporator is nearly excessive.

In the invention, a linear function is applied to the pull down coolingcharacteristic in the first half of pull down cooling. A quadratic orapproximate exponential function is applied to the pull down coolingcharacteristic in the second half of pull down cooling. In the casewhere a linear function is followed, the rotational speed of theinverter compressor is initially low and is gradually increased.Accordingly, an inverter compressor able to cope with unnecessaryhigh-speed rotation or an evaporator with a high heat-radiatingperformance is not provided. On the other hand, rapid refrigeration canbe realized in a second half of pull down cooling requiring an internaltemperature returning force.

<The Invention of Aspect 10>

For example, when pull down cooling is actually used in a refrigeratingstorage cabinet, the conditions of use may have large variations, e. g.an extremely large opening-closing frequency or conversely, the door isalmost never opened or closed. Accordingly, a plurality of programshaving different pull down cooling characteristics is prepared andselectively executed. Consequently, optimum cooling can be performedthat meets the conditions of use.

<The Invention of Aspect 11>

A plurality of pull down cooling characteristics is provided havingdifferent change modes for the physical amount. Each pull down coolingcharacteristic is selectively read and executed.

<The Invention of Aspect 12>

For example, in the case where pull down cooling is performed for afreezer, when the internal temperature is very high, refrigeration issuitable in which the temperature drop is gentle. When the internaltemperature has dropped to some extent, refrigeration causing a largetemperature drop is desirable in order to prevent the deterioration ofthe food material. Furthermore, for the freezing temperature zone (0° C.to −5° C.), the quality of frozen food, such as meat or fish, isimproved when the freezing temperature zone (0° C. to −5° C.) is passedas early as possible.

A plurality of target cooling characteristics is provided in pull downcooling. A suitable one of the target cooling characteristics isselected according to the temperature zone in the interior.Consequently, optimum temperature control is possible over the entirezone of pull down cooling.

<The Invention of Aspect 13>

For example, during operation in the control refrigeration zone, thedoor is frequently opened and closed or warm food is placed into therefrigerating storage cabinet, whereupon the internal temperature risesto a large degree. In this case, the refrigerating storage cabinetproceeds to an operation that conforms to a pull down coolingcharacteristic with a large temperature drop. When the differencebetween the internal temperature and the set temperature is at or belowa predetermined value, a normal pull down cooling characteristic isselected with a relatively smaller temperature drop degree. When thedifference exceeds the predetermined value, a pull down coolingcharacteristic having a relatively larger temperature drop degree isselected. The above is effective when a rapid temperature return isperformed in a case where the internal temperature is outside of thecontrol-cooling zone.

<The Invention of Aspect 14>

The heat-exchange characteristic is deteriorated when an amount of frostformation is on the evaporator. When the operation is continuedfollowing a target-cooling characteristic, the rotational speed of thecompressor needs to be increased, resulting in a waste of power. In viewof this, when the difference between the internal temperature and theevaporation temperature is at or below a predetermined value, anauxiliary cooling characteristic is selected as the pull down coolingcharacteristic to be followed. The auxiliary cooling characteristic hasa temperature curve in which a convergence temperature remains at atemperature that is higher by a predetermined value than the setinternal temperature. More specifically, the above is effective forachieving energy savings without excessive cooling, and also forpreventing frost formation.

Furthermore, when the internal temperature is apart by a predeterminedvalue from the set temperature without following the target-coolingcharacteristic, the above-described auxiliary cooling characteristic isselected. Thus, this control manner can be used as emergency measure.

<The Invention of Aspect 15>

When the pull down cooling zone is changed to the control-cooling zone,the compressor is continuously controlled so as to follow the pull downcooling characteristic. When the internal temperature has dropped to theset temperature, the performance of the compressor is lowered, wherebythe internal temperature gradually drops at a gentler gradient.Thereafter, when the internal temperature has reached the lower limittemperature, the compressor is stopped.

In the control-cooling zone, the internal temperature is rapidlydecreased to the set temperature following pull down cooling.Accordingly, even when the compressor is thereafter operated at a lowerperformance level for energy savings, the internal temperature isdecreased to the lower limit temperature in a suitable time so that thecompressor can be stopped. A defrosting operation is carried out in theevaporator, thereby preventing the formation of a large amount of frost.

<The Invention of Aspect 16>

When the load or the like raises the internal temperature, which wascurrently being decreased from the set temperature to the lower limittemperature, it takes a large amount of time to drop the internaltemperature to the lower limit temperature thereafter. Accordingly, thecompressor is continuously operated for a long period of time. In viewof this, the performance of the compressor is increased when theinternal temperature starts to rise, so that the internal temperaturefalls again to the lower limit temperature. Consequently, the compressorcan be reliably stopped at a suitable time.

BRIEF DESCRIPTION OF THE DRAWINGS

[FIG. 1] A perspective view of the refrigerator-freezer in accordancewith embodiment 1 of the present invention;

[FIG. 2] An exploded perspective view thereof;

[FIG. 3] A diagram of freezing circuit;

[FIG. 4] A partial sectional view of a refrigeration unit;

[FIG. 5] Graphs showing the changes in pressure in a capillary tube;

[FIG. 6] A block diagram of control mechanism of an inverter compressor;

[FIG. 7] A graph showing a pull down cooling characteristic;

[FIG. 8] A flowchart showing a control operation of the invertercompressor;

[FIG. 9] A graph showing changes in the temperature in thecontrol-cooling zone;

[FIG. 10] A graph showing internal temperature characteristics forcomparison of the refrigeration and freezing sides;

[FIG. 11] A graph showing a pull down cooling characteristic inembodiment 2;

[FIG. 12] A flowchart showing a control operation for the invertercompressor;

[FIG. 13] A graph showing a control-cooling characteristic;

[FIG. 14] A figure showing a reference table based on a pull downcooling characteristic in embodiment 3;

[FIG. 15] A flowchart showing a control operation for the invertercompressor;

[FIG. 16] A figure showing a reference table based on a control-coolingcharacteristic;

[FIG. 17] A graph showing a pull down cooling characteristic inembodiment 4;

[FIG. 18] A graph showing a mode of control-cooling in embodiment 5;

[FIG. 19] A graph showing a mode of control-cooling in embodiment 6;

[FIG. 20] A flowchart showing a control operation for the invertercompressor;

[FIGS. 21A and 21B] An explanation and a graph of changes in theinternal temperature in embodiment 7, respectively;

[FIG. 22] A graph showing a cooling control manner in embodiment 8;

[FIG. 23] A graph showing a cooling control manner in embodiment 9;

[FIG. 24] A graph showing a cooling control manner in embodiment 10;

[FIG. 25] A graph showing temperature changes in the control-coolingzone in a related art; and

[FIG. 26] A graph showing temperature curves in the pull down coolingzone in the prior art.

EXPLANATION OF REFERENCE SYMBOLS

30 . . . refrigeration unit (refrigeration device), 32 . . . invertercompressor (compressor), 36 . . . evaporator, 45 . . . control section(control means), 46 . . . internal temperature sensor (physical amountsensor), 49 . . . data storage (storing means), 50 . . . invertercircuit, xp, xp1, xp(1), xp(2), xp(3), xp(a), xp(b), xp(α) ideal curves(pull down cooling characteristics), xc, xc₁ . . . ideal curves(control-cooling characteristic), Sp, Sc . . . actual temperature drop,Ap, Ap₁, Ap₂ . . . target temperature drop degree (pull down cooling),and Ac, Ac₁, Ac₂ . . . target temperature drop degree (control-cooling).

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiments of the present invention will be described with reference tothe attached drawings. The invention is applied to arefrigerator-freezer for commercial use.

Embodiment 1

Embodiment 1 will be described with reference to FIGS. 1 to 10.

The refrigerator-freezer is a four-door type and is provided with a body10 comprising a heat insulating housing having an open front, as shownin FIGS. 1 and 2. A cruciform partition frame 11 partitions the openfront into four access openings 12. Heat insulating walls 13 partitionsubstantially a quarter of the inner space, corresponding to an upperright access opening 12 as viewed from the front, thereby forming afreezing compartment 16. The remaining three quarters of the inner spaceserve as a refrigerating compartment 15. Heat insulating doors 17 arepivotally mounted so as to respectively close and open the accessopenings 12.

An equipment compartment is defined on the top of the body 10 by a panel19 (see FIG. 4) erected around the top of the body. Square openings 21,which have the same size, are formed in the top of the body 10, whichserves as a bottom of the equipment compartment 20, so as torespectively correspond to the ceilings of the refrigerating andfreezing compartments 15 and 16. Refrigeration units 30 are respectivelyadapted to be individually mounted in the openings 21.

Referring to FIG. 3, each refrigeration unit 30 includes a freezingcircuit 31, formed by connecting a compressor 32, a condenser 33 with acondenser fan 33A, a drier 34, a capillary tube 35, and an evaporator36, to one another in a closed loop using refrigerant piping 37, as willbe described in detail later. Furthermore, a heat insulating unit mount38 is mounted to close each opening 21. The evaporator 36, as a part ofthe refrigeration unit 30, is mounted on the lower side of the unitmount 38. The other components of the refrigeration unit 30 are mountedon the upper side of the unit mount 38.

On the other hand, a drain pan 22, which also serves as a refrigeratingduct, is placed near the ceilings of the refrigerating and freezingcompartments 15 and 16 and inwardly inclined downward. An evaporatorcompartment 23 is defined between the unit mount 38 and the drain pan22, as shown in FIG. 4. The drain pan 22 has an inlet port 24 formed inthe upper side thereof. The refrigerating fan 25 is mounted on the upperside of the drain pan 22. The drain pan 22 further has an outlet port 26formed in the lower side thereof.

Upon the powering of the refrigeration unit 30 and the refrigerating fan25, essentially, air in the refrigerating compartment 15 (the freezingcompartment 16) is absorbed through the inlet port 24 and into theevaporator compartment 23, as shown by the arrows in the figure. Whilepassing through the evaporator 36, the air is transformed into chilledair through heat exchange. The chilled air is discharged through theoutlet port 26 into the refrigerating compartment 15 (the freezingcompartment 16), whereby the chilled air is circulated so that theatmosphere is refrigerated in the refrigerating compartment 15 (thefreezing compartment 16).

The intent for the refrigeration units 30, provided for therefrigerating and freezing compartments 15 and 16, is to standardizethem in this embodiment. The following measures are taken for thispurpose.

Firstly, the refrigerating performance of the refrigeration unit 30depends upon the capacity of the compressor. For example, when identicalcompressors are used, the volume refrigerated on the freezing side,where the evaporating temperature is lower, is smaller than on therefrigerating side. Furthermore, a larger refrigerating performance isrequired for either refrigerating or freezing compartments having alarger volume.

More specifically, the required refrigerating performance differsdepending upon the conditions of distinction between refrigeration andfreezing, or the volumes of the compartments. Accordingly, an invertercompressor 32 is used that has the required maximum capacity and acontrollable rotational speed.

Secondly, a common capillary tube 35 is used. The capillary tube 35corresponds to a part from an exit of the drier 34 to the inlet port ofthe evaporator 36, in FIG. 3. The capillary tube 35 includes a centralhelical part 35A, which is provided for increasing the length. The totallength of the capillary tube 35 is set at 2000 mm to 2500 mm in thisembodiment. The refrigerant piping 37 extends from the exit of theevaporator 36 to an inlet of the inverter compressor 32 and has a lengthof about 700 mm. Conventionally, a capillary tube for refrigeration hashigh flow characteristics and a capillary tube for freezing has low flowcharacteristics. In this embodiment, however, the capillary tube 35 hasintermediate flow characteristics, between the refrigeration and thefreezing characteristics.

A capillary tube suitable for refrigeration has flow characteristicssuch that an internal equilibrium temperature, at which the freezingperformance of the refrigeration unit balances the thermal load of theheat insulating housing, ranges from about 0° C. to about −10° C. whenthe refrigeration unit, assembled with the heat insulating housing, isdriven at room temperature. Furthermore, a capillary tube suitable forfreezing has flow characteristics such that an internal equilibriumtemperature ranges from about −15° C. to about −25° C. Accordingly, acapillary tube with intermediate flow characteristics betweenrefrigeration and freezing has flow characteristics such that theinternal equilibrium temperature ranges from about −10° C. to about −20°C. when the refrigeration unit is driven under the same conditions asdescribed above.

When the capillary tube 35 has intermediate flow characteristics asdescribed above, there is a concern that the flow rate of liquidrefrigerant would be inadequate for the refrigeration region. Thefollowing measures are taken in order to resolve that concern.

In this type of freezing circuit, the refrigerant piping 37 at the exitside of the evaporator 36 and the capillary tube 35 are solderedtogether, thereby forming a heat exchanger so that the generalevaporating performance is improved. For example, mist-like liquidrefrigerant, which cannot be evaporated by the evaporator 36, isvaporized. In this embodiment, when the heat exchanger 40 is formedbetween the capillary tube 35 and the refrigerant piping 37, a heatexchanging portion 40A on the capillary 35 side is set at apredetermined area on an upstream side end of the helical portion 35A.The heat exchanging portion 40A is located at a position nearer to theentrance side of the capillary tube 35.

The capillary tube 35 has a large pressure difference between the inletand the outlet thereof. As shown in FIG. SA, the flow resistance isadapted such that it is suddenly increased at a part of the capillarytube 35 where the liquid refrigerant starts to vaporize in the piping(approximately at a central part). In addition, the pressure largelydrops from this part to the downstream side (outlet side). The heatexchanging section of the capillary tube 35 is conventionally set at aposition nearer to the second half of the whole length of the capillarytube, and rather nearer to the outlet of the capillary tube. As aresult, heat exchange is performed even after evaporation (vaporization)starts in the piping. The reason for this is that since the capillarytube 35 is cooled at the side downstream from the heat exchangeposition, and accordingly causes dew condensation and rust, the heatexchange position is located as much as possible to near the outletside, so that the length of exposed portion in the refrigerated state islimited.

In this embodiment, however, the position of the heat exchanging portion40A of the capillary tube 35 is set near to the inlet. Specifically, theheat exchanging portion 40A is located before the position where theliquid refrigerant starts to vaporize. As a result, excessive cooling isincreased such that the boiling start point in the piping can be shiftedto the downstream side of the capillary tube 35, as shown in FIG. 5B.This results in a reduction in the total resistance of the capillarytube 35, whereupon the flow rate of the liquid refrigerant is increasedsubstantially. Consequently, the problem of an insufficient flow rate ofthe liquid refrigerant can be overcome when a capillary tube 35, havingintermediate flow rate characteristics, is used for the refrigeratingregion.

The heat exchanging portion 40A of the capillary tube 35 is locatedbefore the position where the liquid refrigerant starts to vaporize, andat least in the first half region of the whole length of the capillarytube 35, in order that the above-mentioned boiling start point in thepiping may be shifted to the downstream side of the capillary tube 35.Alternatively and more preferably, the heat exchanging portion 40A islocated within a one third region at the inlet side (the region wherethere is a large amount of refrigerant in a liquid state).

Furthermore, when the heat exchanging portion 40A of the capillary tube35 is provided at a position near the inlet, the subsequent longerportion is exposed in a cooling state. Accordingly, this portion isdesired to be spaced as far away as possible from the refrigerant piping37 and to be covered with a heat insulating tube (not shown). As aresult, dew condensation and rust can be prevented.

On the other hand, an accumulator 42 (a liquid separator) is providedclose to the rear of the evaporator 36 in regard to the insufficiency inthrottling in the freezing region when the capillary tube 35 hasintermediate flow characteristics. The accumulator 42 provides anadjustment capacity for storing liquid refrigerant in the refrigeratingcircuit 31.

The refrigerant pressure in the evaporator 36 is lower in the freezingrange (the evaporating temperature of the refrigerant is low) and thedensity of refrigerant gas is low as compared with the pull down coolingrange (a range of quick refrigeration) or the refrigeration range.Accordingly, since the amount of refrigerant circulated by thecompressor 32 is small, there is an excess of liquid refrigerant in thefreezing circuit 31. However, since the excess liquid refrigerant isstored in the accumulator 42, the excess liquid refrigerant can beprevented from flowing into the capillary tube 35 or the like.Consequently, the capillary tube 35 has a substantial effect ofthrottling the flow rate. Thus, insufficiency in throttling can beovercome when the capillary tube 35 has intermediate flowcharacteristics.

Regarding the standardization of the capillary tube 18, the capillarytube 35 is adapted for the freezing range with a low flow rate when thecapillary tube 35 has intermediate flow rate characteristics and anaccumulator 42 is provided directly behind the outlet of the evaporator36 in order to achieve a throttling effect for a reduction in the flowrate of the liquid refrigerant. In addition, the heat exchanging portion40A of the capillary tube 35 is located at the side nearer to the inletso that the total resistance in the piping is reduced, whereby the flowrate of the liquid refrigerant is increased. More specifically, thecapillary tube 35 is adapted to the pull down cooling range with a highflow rate and the refrigeration range.

When the accumulator 42 is provided at the downstream side of the heatexchanging portion 40A of the refrigerant piping 37, there is apossibility that the refrigerant may flow into the heat exchangingportion 40A in a mixed gas-liquid state. In this case, the liquidrefrigerant evaporates. In other words, the heat exchanging portion 40Aperforms the evaporation of the liquid refrigerant as excessive workotherwise conducted by the evaporator 36. This leads to a reduction inthe refrigerating performance in the freezing circuit 1.

In this embodiment, however, the accumulator 42 is provided directlybehind the outlet of the evaporator 36, specifically, at the upstreamside of the heat exchanging portion 40B of the refrigerant piping 37.Accordingly, since only refrigerant gas flows into the heat exchangingportion 40B so that excessive evaporation is not performed, theintrinsic refrigerating performance of the freezing circuit 31 can beensured.

Furthermore, the heat exchanging portion 40A is set at the side nearerto the inlet of the capillary tube 35. As a result, there is a concernthat the flow rate of liquid refrigerant may also be increased on thefreezing side. However, the concern can be overcome as follows.

In the refrigerating circuit 31 with the capillary tube 35, thehigh-pressure side and the low-pressure side basically share therefrigerant. Conceptually, in the refrigeration range the refrigerant isin the condenser 33 and the evaporator 36(including the pull downcooling range), whereas a large amount of refrigerant is in theevaporator 36 and accumulator 42 and a small amount of refrigerant is inthe condenser 33. Accordingly, the refrigerant flows into the capillarytube 35 as a completely liquid flow in the refrigerating range. However,since the refrigerant flows in the mixed gas-liquid state in thefreezing range, the flow rate of the refrigerant is reduced.Accordingly, even when heat exchange is carried out at a position nearerto the inlet of the capillary tube 35 such that excessive coolingoccurs, the flow rate of the refrigerant is not greatly increased.

On the contrary, as a result of the provision of the accumulator 42,there is a possibility that the flow rate may be reduced in therefrigeration range (including the pull down cooling range). However,for a reason opposite to the reason previously provided, the compressor32 circulates a large amount of refrigerant in the refrigeration range(including the pull down cooling range). Accordingly, the amount ofexcess liquid refrigerant in the freezing circuit 31 is small. Becauseof this, only a little liquid refrigerant is stored in the accumulator42. Therefore, it is considered that there is almost no possibility of areduction in the flow rate.

As described above, the refrigeration units 30 employ a common structurefor refrigeration and freezing. On the other hand, the refrigerationunits 30 are individually controlled in operation.

This is based on the perception that a temperature characteristic inpull down cooling changes to a large extent depending upon conditionssuch as the division between refrigeration and freezing or the internalcapacity. In the refrigerators-freezers for commercial use, doors arefrequently opened and closed so that food materials are placed into andtaken out of compartments, and the ambient temperature is relativelyhigher. In view of this, it should be taken into sufficientconsideration that the internal temperature may easily rise.Accordingly, temperature drop characteristics should be considered as areturning force in the internal temperature rise, specifically, pulldown cooling temperature characteristics. Consequently, a performancetest is compulsory for pull down cooling. However, since therefrigeration speed largely depends upon a heat insulating housing asdescribed above, the performance test needs to be conducted with therefrigeration units already assembled with the heat insulating housings.As a result, there is a problem in that the complexity of theperformance test cannot be overcome, even when the refrigeration unitsare standardized.

In this embodiment, means is provided for controlling the internaltemperature along a temperature curve in pull down cooling withoutdependence on the heat insulating housing.

For this purpose, as shown in FIG. 6, a control 45 is provided thatincludes a microcomputer and executes a predetermined program. Thecontrol 45 is enclosed in an electrical equipment box 39 provided on anupper side of the unit mount 38. An internal temperature sensor 46,detecting an internal temperature, is connected to the input side of thecontrol 45.

The control 45 is provided with a clock signal generator 48 and datastorage 49, which stores a linear line ‘a’ of a linear function as anideal temperature curve in pull down cooling, as shown in FIG. 8. Whenthe ideal curve is a linear line ‘a’, a target internal temperature dropdegree (temperature change per unit of time ΔT/Δt) is a predeterminedvalue ‘A’ irrespective of the internal temperature.

An inverter compressor 32 is connected via an inverter circuit 50 to theinput side of the control 45.

Pull down control starts when the internal temperature has risen to orabove a set internal temperature by a predetermined value.

As shown in FIG. 8, an actual internal temperature drop degree ‘B’ isobtained at every detection cycle. The obtained value ‘B’ is comparedwith a target value ‘A’ read from data storage 49. When the obtainedvalue ‘B’ is equal to or below the target value ‘A’, the rotationalspeed of the inverter compressor 32 is increased via the invertercircuit 50. On the other hand, when the obtained value ‘B’ is largerthan the target value ‘A’, the rotational speed of the compressor 32 isreduced. This is repeated at predetermined time intervals so that pulldown cooling is carried out along an ideal curve (linear line xp).

After the above-described pull down cooling, control refrigeration ispreformed for both refrigeration and freezing. As a result, the internaltemperature is maintained at a value close to the previously settemperature. The following advantages can be obtained from provision ofan inverter compressor 32. In the execution of control refrigeration,when the inverter compressor 32 is controlled so that the rotationalspeed thereof is reduced stepwise in the vicinity of the settemperature, the temperature drops quite slowly. As a result, asignificantly longer continuous ON time is generated for the compressor,or in other words, the number of occurrences of ON-OFF switching isreduced to a large extent. Furthermore, low-speed operation results inhigh efficiency and energy saving.

In the above-described case, the refrigerating performance in thelow-speed operation of the inverter compressor 35 needs to be set toexceed an assumed standard thermal load. When the refrigeratingperformance cannot exceed the assumed thermal load, the internaltemperature is not lowered to the set temperature but instead isthermally balanced, remaining at a value above the set temperature. Whena common refrigeration unit 30, including the inverter compressor 32, isused as in this embodiment, the heat insulating housing having thehighest heat invasion amount characteristics needs to be regarded as thethermal load.

Special attention is paid to refrigerators (freezers) for commercial useso that the variations in internal temperature distribution areminimized, in order that the food materials may be stored at apredetermined level of quality. For this purpose, the refrigeration fan23 has the function of circulating a large amount of air. Consequently,a relatively larger amount of heat is generated by the electric motor ofthe fan. When this condition is accompanied with another or otherconditions such as the heat capacity of food materials, ambienttemperature, frequency of door operations and the like, sometimes alarger than expected thermal load is generated. As a result, theinternal temperature may remain at a value slightly lower than a settemperature, even though the inverter compressor 32 is operating at alow-speed, or the ON time may be made excessively long when thetemperature drop results in only a slight change.

It can be considered that there is no problem when the internaltemperature remains at a value slightly lower than the set temperature.However, it is not preferable for the continued operation of therefrigerator while the inverter compressor 32 remains in an on state.The reason for this is that frost continuously falls on the evaporator36 due to outside air entering into the refrigerator with the openingand closing of the doors 17, or due to aqueous vapor emanating from foodmaterial. Conversely, the temperature of the evaporator 36 is increasedto or above 0° C. when the inverter compressor 32 is suitably turnedoff. As a result, it is considered preferable to have a suitable OFFtime in order to maintain the heat exchanging function of the evaporator36.

In this embodiment, energy savings are achieved by taking advantage ofthe use of the inverter compressor 32 in control refrigeration. Withthis, control means is provided to reliably afford an OFF time.

In short, the inverter compressor 32 is controlled in the controlrefrigeration range so that the internal temperature is in alignmentwith an ideal temperature curve, in the same manner as the in theforegoing pull down cooling range. This temperature curve is set aslinear line xc, which has a gentler gradient than the ideal curve(linear line xp) in pull down cooling, as shown in FIG. 9. In the caseof the ideal curve xc, too, the internal temperature drop degree isconstant but smaller than the ideal curve xp.

The ideal curve xc is stored in data storage 49 and used in theexecution of a control refrigeration program that is also stored in thecontrol 45.

Control refrigeration basically has the same operating characteristicsas in pull down cooling. Control refrigeration starts when the internaltemperature has dropped to an upper limit temperature Tu, which ishigher than a set temperature To by a predetermined value. In controlrefrigeration, the internal temperature is detected at intervals ofpredetermined periods. An actual internal temperature drop degree Sc isobtained in synchronization with the detection of the internaltemperature and thereby compared with a target value of the internaltemperature drop degree Sc. The obtained drop rate Sc is compared with atarget value Ac (constant) of the internal temperature drop degree underthe ideal temperature curve xc. When the obtained value Sc is less thanthe target value Ac, the rotational speed of the inverter compressor 32is increased. On the contrary, when the obtained value Sc is larger thanthe target value Ac, the rotational speed of the inverter compressor 32is reduced. This is repeated at intervals of predetermined periods sothat the internal temperature slowly drops along the ideal curve (linearline xc).

The inverter compressor 32 is turned off when the internal temperatureis reduced to a lower limit temperature Td, which is lower than the settemperature To by a predetermined value, whereupon the internaltemperature slowly rises. When the internal temperature returns to theupper limit temperature Tu, temperature control along the temperaturecurve xc is again performed. Thus, the procedure is repeated so that theinterior is maintained about the set temperature To.

According to the control in control refrigeration, refrigeration can beperformed via the use of the inverter compressor 32 together with energysavings, and an OFF time for the inverter compressor 32 can be reliablyensured. As a result, a large amount of frost can be prevented becausethe evaporator 36 performs a defrosting function.

Thus, for example, an operation program Px (refrigeration program Px) isprovided that controls the inverter compressor 32 so that the internaltemperature is in alignment with a temperature characteristic X (seeFIG. 10). This includes the ideal curves xp and xc, from pull downcooling to control refrigeration on the refrigeration side, for example.

On the other hand, at the freezing side, the set internal temperaturediffers from the set internal temperature at the refrigeration side,although the basic control operation at the freezing side is the same asat the refrigeration side. Furthermore, the operating time of theinverter compressor 32 is made shorter at the freezing side than at therefrigeration side in order for the prevention of frost formation duringthe control refrigeration, whereupon an ideal curve at the freezing sidediffers from the ideal curve at the refrigeration side. Accordingly, anoperation program Py (freezing program Py) is required that controls theinverter compressor 32 so that the internal temperature is in alignmentwith a temperature characteristic Y in the aforesaid figure at thefreezing side, for example.

Each refrigeration unit 30 is provided with an equipment box 39 in whichthe control 45 is enclosed. Both of the above-mentioned programs Px andPy are stored in the control 45 together with data of ideal curves.

The embodiment has a structure as described above. The body 10,comprising the heat insulating housing, and two standardizedrefrigeration units 30, separate from the body, are carried to aninstallation site. The refrigeration units 30 are respectively mountedin the openings 21 of the ceilings of the refrigerating and freezingcompartments 15 and 16. Thereafter, when set internal temperatures havebeen respectively supplied to the refrigerating and freezingcompartments 15 and 16. Furthermore, the refrigerating program Px isselected at the control section 45 provided in the refrigeration unit30, attached to the refrigerating compartment 15 side, by switches (notshown) or the like provided in the equipment box 39. On the other hand,the freezing program Py is selected at the control section 45 providedin the refrigeration unit 30 attached to the freezing compartment 16side.

As obvious from the foregoing, the refrigerating and freezingcompartments 15 and 16 are respectively controlled and cooled on thebasis of the individual operation programs Px and Py.

Regarding pull down cooling, for example, the refrigerating compartment15 will be described again. When the internal temperature rises abovethe set temperature by a predetermined value or above, with the openingand closing of the doors or the like, pull down control starts and theinternal temperature is detected at each sampling time. As shown in FIG.8, the degree of actual internal temperature drop Sp is computed on thebasis of the internal temperature detected at every sampling time andcompared with a target value Ap. When the computed value Sp is less thanthe target value Ap, the rotational speed of the inverter compressor 32is increased. For the contrary case, the rotational speed of theinverter compressor 32 is decreased. Speed increases and decreases arerepeated, whereby pull down cooling is performed so as to follow anideal curve (linear line xp). Subsequently, the control operation isexecuted.

The operation is also performed on the freezing compartment 16 side inthe same manner as described above.

Control-cooling will be described again with respect to therefrigerating compartment 15. Control-cooling starts when the internaltemperature drops to the upper limit temperature Tu via pull downcooling. The internal temperature is detected at every sampling time. Asshown in FIG. 8, the degree of actual internal temperature drop Sc iscomputed on the basis of the internal temperature detected at everysampling time and compared with a target value Ac. When the computedvalue Sc is less than the target value Ac, the rotational speed of theinverter compressor 32 is increased. For the contrary case, therotational speed of the inverter compressor 32 is decreased. Speedincreases and decreases are repeated, whereby the internal temperaturegradually drops along an ideal curve (linear line xc). When the internaltemperature drops to the lower limit temperature Td, the invertercompressor 32 is turned off so that the internal temperature maygradually rise. The temperature control is performed again along thetemperature curve xc when the internal temperature returns to the upperlimit temperature Tu. The above temperature control is repeated so thatthe inner atmosphere is substantially maintained about the settemperature To.

Control-cooling is also executed on the freezing compartment 16 side inthe same manner as described above.

The following effects are achieved from this embodiment.

Pull down cooling can be performed at both refrigeration and freezingsides according to the predetermined pull down cooling characteristics,irrespective of conditions such as the capacity of the heat insulatinghousing to which the refrigeration units 30 are attached. Accordingly,the performance test in pull down cooling has no relation with the heatinsulating housing actually used to which the refrigeration unit isattached. For example, a test heat insulating housing can be used forthe performance test. Consequently, the degrees of freedom in the placeand the time of a performance test can be greatly increased.

Furthermore, excessive pull down cooling can be prevented from beingexecuted for a small heat insulating housing. Therefore, theabove-described arrangement can contribute to energy savings.Particularly in this embodiment, the linear line xc of the linearfunction is selected as an ideal temperature curve in pull down cooling.As a result, calculation is not required since the target physicalamount reduction degree is constant, irrespective of the lapse of time.Accordingly, the control system can be simplified.

Furthermore, since the internal temperature is gradually decreased at agentle gradient or along an ideal curve (linear line xc) incontrol-cooling, the continuous ON time of the inverter compressor 32 ismade longer. In other words, the number of ON-OFF switching cycles ofthe inverter compressor 32 is greatly reduced. In addition, since theinverter compressor is operated at low speeds, high efficiency andenergy savings can be achieved. On the other hand, since the lower endof the ideal curve (linear line xc) reaches the lower limit temperatureTd, the inverter compressor 32 can be reliably stopped for suitableintervals of time. During the stopping of the inverter compressor 32,the evaporator 36 can perform a defrosting function so that a largeamount of frost formation can be prevented.

Particularly in this embodiment, the linear line xc of a linear functionis selected as the ideal temperature curve in control-cooling. As aresult, calculation is not required since the target physical amountreduction degree is constant, irrespective of the lapse of time.Accordingly, the control system can be simplified.

In the practical use of the refrigerating storage cabinet, there aresituations in which the formation of frost greatly differs, dependingupon conditions such as the installation location, the frequency atwhich the door is opened and closed, or the types of food to be stored.Accordingly, a plurality of programs is available, differing from eachother in the operating time of the inverter compressor 32. When eachprogram is selectively performed according to the conditions of use, anoptimum control-cooling can be performed according to those conditions.

Embodiment 2

Embodiment 2 of the present invention will be described with referenceto FIGS. 11 to 13.

In embodiment 2, an ideal temperature curve in pull down cooling isformed by the curve xp1 of a quadratic function involving a physicalamount and time, as shown in FIG. 11. When a constant speed compressoris used, the temperature drop characteristic in pull down cooling isgenerally represented as a quadratic function curve. On the other hand,this temperature drop characteristic has had real accomplishments in themarket and has earned a fine reputation from its users. Thischaracteristic is used as an ideal curve xp₁.

In the case of the quadratic function curve xp₁, the degree of targettemperature drop is not constant, but differs depending upon theinternal temperature. Accordingly, a computing section is provided forcomputing the target temperature drop degree. More specifically, in thecomputing section a target temperature drop degree Ap₁ is computed fromthe above quadratic function curve xp₁ as a temperature drop amount(ΔT/Δt) per unit of time in the internal temperature, thereby beingprovided. The temperature drop degree Ap₁ may be obtained from thedifferentiation (dT/dt) of the quadratic function curve xp₁.

The operation is as follows. Pull down control starts when the internaltemperature rises so that the internal temperature is detected at everysampling time. The actual internal temperature drop degree Sp iscomputed on the basis of the internal temperature detected at everysampling time, as shown in FIG. 12. On the other hand, the targettemperature drop degree Ap₁ at the current internal temperature iscomputed from the quadratic function curve xp₁ in the computing section.The computed target value Ap₁ is compared with the actual temperaturedrop degree Sp. When the actual temperature drop degree Sp is less thanthe target value Ap₁, the rotational speed of the inverter compressor 32is increased. For the contrary case, the rotational speed of theinverter compressor 32 is decreased. The speed increases and decreasesare repeated so that pull down cooling is performed along the idealcurve (quadratic function curve xp₁). Subsequently, control-cooling isexecuted. The same operations can also be performed on the freezingcompartment 16 side.

Accordingly, pull down cooling can be performed on the basis of atemperature drop characteristic that has had real accomplishments in themarket and has earned a fine reputation from its users.

Additionally, instead of comparing the target value Ap₁ with the actualtemperature drop degree Sp obtained at each sampling time, an averagevalue of the target values Ap₁ may be compared with an average value ofthe actual temperature drop degree Sp obtained every time, after thepassage of several sampling cycles. For example, a more accurate controlcan be achieved that is not so easily influenced by a temporary changein the internal temperature.

The ideal curve xp1 of quadratic function curve in the embodiment 2 hasa target temperature drop degree changing from moment to moment. Forexample, a temperature curve of pull down cooling in a no-load conditioncan be applied in an actual refrigerator (no articles to be refrigeratedin the refrigerator-freezer).

The target temperature drop degree is required in order that atime-temperature characteristic on the ideal curve may be directlyreproduced. This involves the following intention: for example, in acase where pull down cooling is performed as a trial operation on acustomer site after installation, a refrigerator with a constant speedcompressor, without an inverter, is quite typical when the refrigeratoroperates in the same manner as a model refrigerator (temperaturechanging manner).

Furthermore, as described above, an ideal curve of a model refrigeratorin a no-load condition is applied to the ideal curve for control.Accordingly, for example, when food material is placed into therefrigerator, the degree of temperature drop slows down and becomessmaller than the target temperature drop degree. Since the invertercompressor is controlled so that the rotational speed thereof isincreased in order to compensate for the slowdown, the coolingperformance is increased. In short, the rotational speed of the invertercompressor 32 tends to be increased as a larger amount of food materialis placed in the refrigerator. This demonstrates the high performance ofthe refrigerator. Since the refrigerator behaves as if the entry of foodmaterial were detected, the above control manner is called a “sensorlesscontrol.”

Furthermore, when the ideal curve of pull down cooling is a quadraticfunction curve, a steep gradient occurs in the start-up. As a result,articles can be quickly refrigerated. In addition, the gradient becomesgentler when the internal temperature approaches near to the settemperature. As a result, overshooting or excessive cooling can beprevented.

Additionally, an ideal temperature curve in control-cooling may also beformed by the temperature-time curve xc₁ of a quadratic function(T=f(t)), as shown in FIG. 13. On the average, as with the linear linexc in embodiment 1, the curve xc₁ represents a gradual temperaturereduction.

In the case of the quadratic function curve xc₁, however, a targettemperature drop degree is not constant, but instead differs dependingupon the internal temperature. Accordingly, a computing section isprovided for computing the target temperature drop degree. Morespecifically, in the computing section a target temperature drop degreeAc₁ is computed as a temperature drop amount (ΔT/Δt) per unit of time inthe internal temperature from the above quadratic function curve xc₁,thereby being produced. The temperature drop degree Ac₁ may be obtainedas the differentiation (dT/dt) of the quadratic function curve xc₁.

In operation, the refrigerator proceeds to control-cooling when theinternal temperature drops to the upper limit temperature Tu. Theinternal temperature is detected at every predetermined sampling cycle.An actual internal temperature drop degree Sc is computed on the basisof the detected internal temperature at every sampling time, as shown inFIG. 12. On the other hand, the target temperature drop degree Ac₁ atthe current internal temperature is computed in the computing sectionusing the quadratic function curve xc₁. The computed target value Ac₁ iscompared with the actual temperature drop degree Sc. When the actualtemperature drop degree Sc is less than the target value Ac₁, therotational speed of the inverter compressor 32 is increased. For thecontrary case, the rotational speed of the inverter compressor 32 isdecreased. The speed increases and decreases are repeated so that pulldown cooling is performed along an ideal curve (quadratic function curvexc₁). Subsequently, control-cooling is executed. The same operations canalso be carried out at the freezing compartment 16 side.

As in embodiment 1, control-cooling can be performed with energysavings. In addition, an operation stop time of the inverter compressor32 can be reliably provided at suitable intervals.

Furthermore, an ideal curve of pull down cooling may be the quadraticfunction curve xp₁, and an ideal curve of control-cooling, continuingfrom pull down cooling, may be the linear line xc of a linear function,as shown in embodiment 1 above.

Embodiment 3

FIGS. 14 to 16 illustrate embodiment 3 of the invention. In embodiment3, the target temperature drop degree Ap₂, corresponding to an internaltemperature, is previously obtained on the basis of an ideal pull downcooling characteristic. A reference table relating the internaltemperature with the target temperature drop degree Ap₂ is generatedbeforehand and stored in a data storing section 49, as shown in FIG. 14.

The operation of embodiment 3 is as follows. Upon the start of pull downcontrol, the internal temperature is detected at each predeterminedsampling time. As shown in FIG. 14, the actual internal temperature dropdegree Sp is computed on the basis of the detected internal temperatureat every sampling time. A target temperature drop degree Ap₂ for thecurrent internal temperature is retrieved from the reference table,thereby to be provided. The delivered target value Ap₂ is compared withthe actual internal temperature drop degree Sp. When the actual internaltemperature drop degree Sp is less than the target value Ap₂, therotational speed of the inverter compressor 32 is increased. For thecontrary case, the rotational speed of the inverter compressor 32 isdecreased. The speed increases and decreases are repeated so that pulldown cooling is performed following along an ideal pull down coolingcharacteristic. Subsequently, control operation is executed. Theoperations are executed in the same manner on the freezing compartment16 side.

In embodiment 3, a temperature drop characteristic that has had realaccomplishments in the market and has earned a fine reputation from itsusers, as exemplified in embodiment 2, can be applied as an ideal pulldown cooling characteristic.

In particular, the target temperature drop degree Ap₂ is obtained onlythrough the retrieval of the reference table, no computation isrequired. As a result, the control speed can be increased.

Furthermore, a target temperature drop degree Ac₂, corresponding to aninternal temperature, is previously obtained on the basis of an idealcontrol-cooling characteristic. A reference table relating the internaltemperature with the target temperature drop degree Ac₂ is previouslyproduced and stored in the data storing section 49, as shown in FIG. 16.A temperature that can belong to the control-cooling zone serves as theinternal temperature stored in the reference table.

In operation, upon the start of control-cooling, the internaltemperature is detected at each sampling time. As shown in FIG. 15, theactual internal temperature drop degree Sc is computed on the basis ofthe detected internal temperature at every sampling time. A targettemperature drop degree Ac₂ at the current internal temperature isretrieved from the reference table, thereby to be provided. The providedtarget value Ac₂ is compared with the actual internal temperature dropdegree Sc. When the actual internal temperature drop degree Sc is lessthan the target value Ac₂, the rotational speed of the invertercompressor 32 is increased. For the contrary case, the rotational speedof the inverter compressor 32 is decreased. The speed increases anddecreases are repeated so that control-cooling is performed to followalong an ideal pull down cooling characteristic (approximate quadraticfunction, for example). The operations are executed in the same manneron the freezing compartment 16 side.

As in embodiments 1 and 2, control-cooling can be performed with energysavings, and an operation stop time for the inverter compressor 32 canbe reliably provided at suitable intervals. In the same way, thereference table is only retrieved in order to obtain the targettemperature drop degree Ac₂, but no computation is required. As aresult, the control speed can be increased.

Embodiment 4

FIG. 17 illustrates embodiment 4 of the invention. Embodiment 4 isdirected to pull down cooling. For example, in a refrigerator with a setinternal temperature of 3° C., it is rare for the internal temperatureto rise to 15° C. or 20° C., even though the door may be frequentlyopened and closed, or a large amount of warm food material is placedwithin the refrigerator. It is the zone at or lower than 20° C. or 15°C. that requires a returning force. In this zone, rapid refrigerationfollowing a pull down cooling characteristic of a quadratic function isdesirable. However, when a quadratic function is applied to the zone ator higher than 20° C. or 15° C. (first half of pull down cooling), alarge cooling performance is required. Accordingly, the invertercompressor 32 able to cope with high-speed rotation or an evaporator 33with a large capacity is required. In other words, in order to cope withthe first half of pull down cooling, which has low frequency and is lessimportant, the provision of the above inverter compressor or evaporatoris almost excessive.

Accordingly, in embodiment 4, a linear function xp (see embodiment 1) isapplied to a pull down cooling characteristic in the first half of pulldown cooling. A quadratic (see embodiment 2) or an approximateexponential (reference table type; see embodiment 3) function xp₁ isapplied to the pull down cooling characteristic in the second half ofthe pull down cooling.

In the case where the linear function xp is followed, the rotationalspeed of the inverter compressor is initially low and graduallyincreased. Accordingly, the inverter compressor 32 able to cope with anunnecessary high-speed rotation or an evaporator 33 with a highheat-radiating performance is not provided. On the other hand, rapidrefrigeration can be realized in the second half of pull down coolingrequiring an internal temperature returning force.

Embodiment 5

Embodiment 5 of the invention will be described with reference to FIG.18. As exemplified in embodiment 1, pull down cooling is performed so asto follow an ideal pull down cooling characteristic (linear line xp) inthe pull down cooling zone. In embodiment 5, however, even when theinternal temperature reaches the upper limit temperature Tu and entersthe control-cooling zone, pull down cooling is continued, following thecooling characteristic xp with the inverter compressor 32 under speedcontrol, until the set temperature To is reached.

The control on the basis of the cooling characteristic xp ends when theinternal temperature has dropped to the set temperature To. At the sametime, the rotational speed of the inverter compressor 32 is reduced.Subsequently, the internal temperature gradually drops. The invertercompressor 32 is turned off when the internal temperature has reachedthe lower limit temperature Td. When the internal temperature graduallyrises, returning to the upper limit temperature Tu, control on the basisof the above cooling characteristic (linear line xp) is performed untilthe internal temperature reaches the set temperature To and therotational speed of the inverter compressor 32 is reduced. The aboveoperation is repeated so that the interior is maintained approximatelyabout the set temperature To.

The internal temperature is decreased to the set temperature To for theperiod following pull down cooling when the internal temperature hasentered the control-cooling zone. Accordingly, even when the invertercompressor 32 is operated at low speeds for energy savings, the internaltemperature reliably drops to the lower limit temperature Tu. Afterwhich, the inverter compressor 32 can be stopped. Similarly, adefrosting operation is performed in the evaporator 36 such that a largeamount of frost formation can be prevented. The same control can also beexecuted on the freezing compartment 36 side.

Embodiment 6

FIGS. 19 and 20 illustrate embodiment 6. Embodiment 6 provides animprovement of embodiment 5. In the above embodiment 5, the internaltemperature is decreased to the set temperature To in a single period.Thereafter, the rotational speed of the inverter compressor 32 isreduced so that the internal temperature gradually drops to the lowerlimit temperature Tu. When variations in the load or the like cause theinternal temperature to rise in the middle of a temperature drop, ittakes a great deal of time for the internal temperature to drop to thelower limit temperature Td. Accordingly, there is the creation ofconcern that the continuous ON time of the inverter compressor 32 willbecome unduly long.

In view of this problem, embodiment 6 provides a control function forcompensation. In describing the operation, as shown in FIG. 19, therotational speed of the inverter compressor 32 is reduced after theinternal temperature has dropped to the set temperature To. Whenentering a (spontaneous) temperature drop zone, the internal temperatureis detected at every sampling time. As shown in FIG. 20, the actualinternal temperature drop degree Sc is computed on the basis of theinternal temperature detected at every sampling time. The invertercompressor 32 is maintained at the current rotational speed when thecomputed value Sc is positive or when the internal temperature hasdropped.

Conversely, when the actual internal temperature drop degree Sc isnegative (including zero), the internal temperature is regarded ashaving reversed direction, rising in the middle, as shown by the brokenlines in FIG. 19. The rotational speed of the inverter compressor 32 isincreased. As a result, the internal temperature again drops. Therotational speed of the inverter compressor 32 is repeatedly increasedwhen necessary, whereby the internal temperature is forced to reliablydrop to the lower limit temperature Td.

Additionally, when the actual internal temperature drop degree Sc ispositive, namely, the internal temperature is regarded as havingreversed direction and dropping, the rotational speed of the invertercompressor 32 may be reduced towards a speed at which the compensationcontrol starts.

Embodiment 7

Embodiment 7 of the invention will be described with reference to FIG.21. When the temperature of the heat insulating housing reduces from T₁to T₂ due to heat radiation, as shown in FIG. 21A (T₁>T₂), in many casesthe temperature T in the housing is approximated by an exponentialfunction curve, as shown by the following equation and in FIG. 21B:T=T ₂−(T ₂ −T ₁) e ^(−At)where A is a constant. Accordingly, an exponential function curve may beused as the target temperature curve in pull down cooling andcontrol-cooling. The operation of embodiment 7 is similar to that ofembodiment 2.

Embodiment 8

FIG. 22 illustrates embodiment 8 of the invention. Embodiment 8 showsanother control example in pull down cooling. In short, a plurality oftarget temperature curves in pull down cooling is stored. An optimumtemperature curve is selected according to the changes in the internaltemperature. The control is performed so as to follow the temperaturecurve.

For example, in a case where pull down cooling is performed for afreezer when the internal temperature is high (at or above 20° C., forexample) and the freezer is heavily loaded, it is accordingly proper toapply a temperature curve xp(1) with a gentle temperature drop. When theinternal temperature has dropped to some extent, it is then desirable tofollow a temperature curve xp(2) with a larger temperature drop, sincethe food material should be prevented from deterioration by rapidcooling. In addition, for the freezing temperature zone in the freezer(particularly, in the range from 0° C. to −5° C.), it is known that thequality of frozen foods, such as meat or fish, is improved when thefreezing temperature zone (0° C. to −5° C.) is traversed as early aspossible. In this zone, the evaporating temperature (low pressure) isalso reduced. As a result, the operation of the inverter compressor athigh speeds does not result in heavy loads. Consequently, it ispreferable to select a temperature curve xp(3) with an even largertemperature drop for the zone.

Therefore, a plurality of target cooling characteristics is provided inpull down cooling. A suitable one of the target cooling characteristicsis selected according to the temperature zone in the interior.Therefore, optimum temperature control is possible over the entire zoneof pull down cooling.

Embodiment 9

FIG. 23 illustrates embodiment 9 of the invention. In embodiment 9, aplurality of target cooling characteristics is also provided in pulldown cooling. One temperature curve is selected on the basis of thedifference between the set internal temperature and the current internaltemperature. An effective use is as a returning means against atransient temperature rise in control-cooling.

For example, during operation in the control refrigeration zone, thedoor is frequently opened and closed or warm food is placed within therefrigerating storage cabinet. Consequently, the internal temperaturerises to a large degree. In this case, the refrigerating storage cabinetproceeds from the control-cooling zone to the pull down cooling zone,for example, in embodiment 1. As a result, since the target temperaturecurve is also changed to a curve with a large temperature drop (xp), theoperation usually restores the internal temperature.

However, when the door is opened and closed excessively per unit of timeor the amount of food material placed within the freezer is excessivelylarge, or the temperature of the food material is high, the internaltemperature, which may be sufficiently higher than the set temperature(3° C.), for example, such as 10° C. (difference is 7° C.), isunsuitable for the storage of food material.

Accordingly, as shown in FIG. 23, when the internal temperature hasreached a value 7° C. higher than the set internal temperature (3° C.),the normal temperature curve xp(a) for pull down cooling is changed to atemperature curve xp(b), having a temperature drop degree of 1.5 to 3times greater than the normal curve. The operation is controlled so asto follow the temperature curve xp(b). As a result, the internaltemperature can quickly be restored.

In this case, when the internal temperature has been restored andreaches the control-cooling zone, the temperature curve is againreverted to the control-cooling temperature curve xc. Additionally, thetemperature curve xp(b), with a higher temperature drop degree, iscanceled.

Therefore, the above is effective when a rapid temperature return isperformed in the case where the internal temperature has shifted by alarge extent from the control-cooling zone.

Embodiment 10

Embodiment 10 of the invention will be described with reference to FIG.24. The heat-exchange characteristic of an evaporator 36 is reduced whena large amount of frost is attached to the evaporator 36 in therefrigerating storage cabinet of this type. When the operation iscontinued following a target cooling characteristic (temperature curve)xp or xc while the evaporator 36 is frosted, the rotational speed of theinverter compressor 32 needs to be increased so that the evaporatingtemperature is decreased. Thereby, the difference is increased betweenthe internal temperature and the evaporating temperature. However, thisresults in a waste of electric power even though the internaltemperature and the internal temperature drop can be maintained.

Accordingly, when the difference between the internal temperature andthe evaporating temperature exceeds a predetermined value, for example,17° C. (normally, about 10° C.), the temperature curve to be followed ischanged to a temperature curve xp(a), as shown in FIG. 24. In addition,the control is executed so that the internal temperature becomesslightly higher than the set temperature. For example, an internaltemperature of 8° C., which is 5° C. higher than the set temperature of3° C., may be maintained by the temperature curve.

In short, the intention is to achieve energy savings without excessivecooling of the interior and at the same time prevent frost formation.

The defrosting operation may be forced when the difference between theinternal temperature and the evaporating temperature exceeds apredetermined value (17° C.)

Furthermore, the above-described temperature curve xp(α) may be used asthe target temperature curve in an emergency evacuation. For example,the maximum rotational speed of the inverter compressor 32 is notmaintained, but instead a gentler temperature curve xp(α) is selected inan emergency evacuation. This happens when cooling along the targettemperature curve xp or xc cannot be performed for the reason that theoriginal cooling performance is insufficient against the load, theevaporator 36 is frosted, or refrigerant leaks (the actual cooling stateis shown by the temperature curve xpr in the figure). After the lapse ofa predetermined time, the temperature curve xp or xc is re-selected.When the temperature curve cannot be followed at this time, therefrigerator may be used to deliver a failure diagnosis signal.

Related Technique

The following control may be executed so that energy savings is realizedby taking advantage of using the inverter compressor 32 incontrol-cooling and then providing an OFF time. As shown by the solidline graph in FIG. 25, the inverter compressor 32 is forced to be turnedoff when a timer measures a predetermined ON time of the invertercompressor 32.

Furthermore, as shown by the broken line graph in this figure, therotational speed of the inverter compressor 32 may be increased when atimer measures a predetermined ON time of the inverter compressor 32. Asa result, the internal temperature is forced to decrease to the lowerlimit temperature Td, whereby the inverter compressor 32 is turned off.In this case, since the internal temperature is decreased once to thelower limit temperature, the OFF time of the inverter compressor 32 isrendered relatively long as compared with a forced turn-off.

Other Embodiments

(1) A time-varying mode of internal temperature is exemplified as acooling characteristic to be followed in the foregoing embodiments.However, a measure or standard may be used on the side of therefrigeration unit, for example, the low pressure of the refrigerant orthe time-varying mode of the evaporating temperature.

(2) In the foregoing embodiments, the inverter compressor is used as ameans for adjusting the refrigerating performance of the refrigerationunit. The means should not be limited to the above. A compressor havingmultiple numbers of cylinders and an unload function in which the numberof driven cylinders is adjusted according to the load, and othervariable capacity type compressors may be used.

(3) The present invention should not be limited to the case where therefrigeration unit is common to refrigeration and freezing. The presentinvention may be applied to a case where the refrigeration unit isdedicated to refrigeration or freezing. A desired pull down cooling canbe performed in the individual refrigerating storage cabinets.

(4) Furthermore, a refrigerating apparatus may not be unitized. Acompressor, evaporator, or the like, may be attached to therefrigerating apparatus.

1-16. (canceled)
 17. A refrigerating storage cabinet for refrigerating an inner atmosphere and including a refrigeration unit comprising a compressor and an evaporator, in which the refrigerating storage cabinet comprises: a storing means for storing a cooling characteristic comprising a target physical amount as a function of operating time; a physical amount sensor able to detect a physical amount, corresponding to the target physical amount, at predetermined intervals of operating time; wherein the compressor comprises a plurality of performance levels; an operation control means for controlling the compressor by selecting an appropriate one of the plurality of performance levels based upon a relationship between the physical amount and the target physical amount for a corresponding operating time.
 18. The refrigerating storage cabinet of claim 17, wherein: the physical amount and the target physical amount are temperatures; wherein the physical amount is the temperature of the inner atmosphere; wherein the compressor is controlled by the operation control means in which the cooling characteristic is a pull down characteristic while the physical amount is in a temperature range from above a high temperature to near a set temperature; wherein the high temperature is higher than the set temperature by more than a predetermined value.
 19. The refrigerating storage cabinet of claim 18, comprising: an upper limit temperature that is higher by the predetermined value than a set temperature; a lower limit temperature that is lower by the predetermined value than the set temperature; a control-cooling zone between and including the upper limit temperature to the lower limit temperature; wherein when the physical amount is in the control-cooling zone, the cooling characteristic is a control-cooling characteristic; wherein the compressor is controlled by the operation control means wherein the control characteristic is a control-cooling characteristic when the physical amount is in the control-cooling zone from the upper limit temperature to the lower limit temperature; wherein when the physical amount reaches the lower limit temperature from a temperature higher than the lower limit temperature, the compressor is not operated; wherein when the physical amount reaches the upper limit temperature from a temperature lower than the upper limit temperature, the compressor is operationally controlled by the operation control means.
 20. The refrigerating storage cabinet according to claim 19, characterized in that the compressor is a speed-controllable inverter compressor, and the operation control means comprises: a physical amount change computing section computing a physical amount reduction degree at the predetermined intervals of operating time; a target physical amount reduction degree output section providing a target physical amount reduction degree corresponding to the predetermined intervals of operating time; a comparing section for comparing the physical amount reduction degree to the target physical amount reduction degree at a corresponding operation time; and a speed control section controlling the inverter compressor so that a rotational speed of the inverter compressor is increased when the comparing section indicates that the physical amount reduction degree is smaller than the target physical amount reduction degree, and decreasing the rotational speed of the inverter compressor when the comparing section indicates that the actual physical amount reduction degree is larger than the target physical amount reduction degree.
 21. The refrigerating storage cabinet according to claim 20, characterized in that the pull down characteristic is a linear function; wherein the target physical amount reduction degree is a constant value.
 22. The refrigerating storage cabinet according to claim 21, characterized in that the control-cooling characteristic is a linear function; wherein the target physical amount reduction degree is a constant value.
 23. The refrigerating storage cabinet of claim 20, characterized in that the control-cooling characteristic is a linear function.
 24. The refrigerating storage cabinet of claim 20, characterized in that the control-cooling characteristic is a quadratic function; and wherein the pull down characteristic is a quadratic function.
 25. The refrigerating storage cabinet of claim 20, characterized in that the control-cooling characteristic is represented as an exponential function; and wherein the pull down characteristic is an exponential function.
 26. The refrigerating storage cabinet of claim 20, further characterized by a reference table in which the target physical amount reduction degrees have been determined for a plurality of target physical amounts and stored in the reference table according to an associated target physical amount; an appropriate target physical amount reduction degree is retrieved by the target physical amount reduction degree output section from the target reduction table based on a correspondence between the physical amount and the associated target physical amount; a physical amount change computing section computing a physical amount reduction degree for the physical amount based on the physical amount and a previously measured physical amount; wherein the physical amount reduction degree and the appropriate target physical amount reduction degree are used as inputs for the comparing section.
 27. The refrigerating storage cabinet of claim 19, characterized in that the control-cooling characteristic is a quadratic function.
 28. The refrigerating storage cabinet of claim 19, characterized in that the control-cooling characteristic is represented as an exponential function.
 29. The refrigerating storage cabinet of claim 20, wherein the pull down cooling zone includes a first pull down zone and a second pull down zone; wherein the pull down characteristic includes a first pull down characteristic and a second pull down characteristic wherein the first pull down characteristic is used for the first pull down zone and is a linear function; wherein the second pull down characteristic is used for the second pull down part and is a quadratic function.
 30. The refrigerating storage cabinet of claim 17, wherein the storing means stores a plurality of the cooling characteristics; wherein the operation control means executes an appropriate one of the cooling characteristics based upon the physical amount.
 31. The refrigerating storage cabinet of claim 18, characterized in that a plurality of the pull down cooling characteristics is provided; wherein an appropriate one of the plurality of the pull down cooling characteristics is executed based on the physical amount.
 32. The refrigerating storage cabinet of claim 31, wherein the appropriate one of the plurality of the pull down cooling characteristics is executed based upon a zone of the physical amount
 33. The refrigerating storage cabinet of claim 31, wherein the appropriate one of the plurality of the pull down cooling characteristics includes a small temperature drop degree when a difference between the physical amount and the target physical amount is less than a predetermined value; and wherein the appropriate one of the plurality of the pull down cooling characteristics includes a large temperature drop degree when the difference between the physical amount and the target physical amount is greater than or equal to the predetermined amount.
 34. The refrigerating storage cabinet of claim 31, characterized in that the plurality of the pull down cooling characteristics includes an auxiliary cooling characteristic comprising a temperature curve in which a convergence temperature remains at a temperature higher by an auxiliary predetermined value than the set internal temperature; wherein the auxiliary cooling characteristic is selected as the appropriate one of the plurality of the pull down cooling characteristics when a difference between the physical amount and an evaporation temperature of the evaporator is at or above a predetermined auxiliary temperature value or when the physical amount is higher than the target physical amount by a predetermined auxiliary temperature value.
 35. A refrigerating storage cabinet for refrigerating an inner atmosphere and including a refrigeration unit comprising a compressor and an evaporator, in which the refrigerating storage cabinet comprises: a storing means for storing a plurality of cooling characteristics comprising a target physical amount as a function of operating time; a physical amount sensor able to detect a physical amount, corresponding to the target physical amount, at predetermined intervals of operating time; wherein the compressor comprises a plurality of performance levels; an operation control means for controlling the compressor by selecting an appropriate one of the plurality of performance levels based upon a relationship between the physical amount and the target physical amount for a corresponding operating time; wherein the operation control means selects an appropriate one of the plurality of cooling characteristics based upon the physical amount; wherein the target physical amount is determined from the appropriate one of the plurality of cooling characteristics.
 36. The refrigerating storage cabinet of claim 35, wherein: the physical amount and the target physical amount are temperatures; wherein the physical amount is the temperature of the inner atmosphere; wherein the compressor is controlled by the operation control means in which the cooling characteristic is a pull down characteristic while the physical amount is in a temperature range from above a high temperature to near a set temperature; wherein the high temperature is higher than the set temperature by more than a predetermined value; an upper limit temperature that is higher by the predetermined value than a set temperature; a lower limit temperature that is lower by the predetermined value than the set temperature; a control-cooling zone between and including the upper limit temperature to the lower limit temperature; wherein when the physical amount is in the control-cooling zone, the cooling characteristic is a control-cooling characteristic; wherein the compressor is controlled by the operation control means wherein the control characteristic is a control-cooling characteristic when the physical amount is in the control-cooling zone from the upper limit temperature to the lower limit temperature; wherein when the physical amount reaches the lower limit temperature from a temperature higher than the lower limit temperature, the compressor is not operated; wherein when the physical amount reaches the upper limit temperature from a temperature lower than the upper limit temperature, the compressor is operationally controlled by the operation control means. 